WO2012117597A1 - Multistage pressure condenser and steam turbine plant equipped with same - Google Patents

Abstract

A multistage pressure condenser equipped with: a pressure bulkhead (4), which has multiple holes (8) and partitions a low-pressure-side low-pressure chamber (2) in the vertical direction; a cooling pipe group (5), which is provided in the upper part of the low-pressure chamber (2) partitioned by the pressure bulkhead (4), and which condenses low-pressure-side steam into low-pressure-side condensate by means of the exchange of heat between cooling water introduced into the pipe group and low-pressure-side steam introduced into the low-pressure chamber (2); a reheating chamber (6), which is the lower part of the low-pressure chamber (2) partitioned by the pressure bulkhead (4), and in which low-pressure-side condensate flowing down through the holes (8) in the pressure bulkhead (4) accumulates; a high-pressure-side steam introduction means (11) that introduces the high-pressure-side steam in a high-pressure-side high-pressure chamber (22) into the reheating chamber (6); and multiple plate-shaped members (10) arranged beneath the pressure bulkhead (4) parallel to each other in the direction in which the low-pressure-side condensate flows down from the holes (8) in the pressure bulkhead (4). The cross section of each plate-shaped member (10) in the direction of flow of the low-pressure-side condensate forms at least one concavo-convex shape.

Description

Multistage condenser and steam turbine plant equipped with the same

The present invention relates to a multi-stage pressure condenser used in a steam turbine plant.

Generally, in a steam turbine plant or the like, the steam that drives the steam turbine is exhausted from the turbine and guided to a condenser. The steam led to the condenser is condensed by exchanging heat with the cooling water led to the condenser and condensed. The condensed water condensed in the condenser is heated via the heater and supplied to the boiler. The heated condensate supplied to the boiler is converted into steam and used as a drive source for the steam turbine.

In such a steam turbine plant, the higher the condensate temperature led from the condenser to the heater, the higher the plant efficiency, or the amount of cooling water used for heat exchange in the condenser A multi-stage condenser is used.

FIG. 5 shows a schematic configuration diagram of a two-stage multi-stage pressure condenser including, for example, a high-pressure and a low-pressure condenser.
Of the multistage pressure condenser 1 composed of a high-pressure and low-pressure condenser, the low-pressure condenser 2 has a porous partition 8 that divides the longitudinal direction of the low-pressure cylinder 3 into an upper part and a lower part. 4, a low-pressure side cooling pipe group 5 provided on the upper side of the low-pressure side cylinder 3 to which the cooling water is guided, and a reheating chamber 6 positioned below the low-pressure side cylinder 3.

Exhaust gas (low-pressure side steam) from a steam turbine (not shown) guided to the upper side of the low-pressure side cylinder 3 is condensed by heat exchange with cooling water guided to the low-pressure side cooling pipe group 5, and is recovered. It becomes water and is stored above the pressure bulkhead 4 to form a condensate pool 7. Since the pressure partition wall 4 is provided with a plurality of holes 8, the low-pressure side condensate flows down from the condensate pool 7 to the reheat chamber 6.

The reheat chamber 6 is connected to a steam duct 13 that guides the exhaust of the steam turbine above the high pressure side condenser 22 to the reheat chamber 6 of the low pressure side condenser 2. Therefore, the low-pressure side condensate flowing down to the reheating chamber 6 comes into gas-liquid contact with the high-pressure side steam guided from the steam duct 13 and is reheated. The reheat efficiency improves as the time during which the low-pressure condensate to be reheated is in gas-liquid contact with the exhaust of the high-pressure side steam increases.

In order to increase the gas-liquid contact time, Patent Document 1 discloses providing a tray 9 for storing and overflowing the low-pressure side condensate flowing down from the porous 8 in the reheating chamber 6 as shown in FIG. ing.
Further, Patent Document 2 discloses that an angle steel with its apex facing upward or a spiral element is suspended from a pressure bulkhead.
Further, Patent Document 3 discloses that a cylindrical liquid film extending in the longitudinal direction of the low-pressure side cylinder is suspended from the pressure partition into the reheat chamber.

Japanese Patent No. 3706571 JP 2009-52867 A Japanese Patent Laid-Open No. 11-173768

However, in recent years, it is desired to improve the reheat efficiency by increasing the gas-liquid contact time further than the invention disclosed in Patent Document 1 to Patent Document 3.

Further, in the case of the invention disclosed in Patent Document 1 to Patent Document 3 and FIG. 5, when the in-body pressure difference between the high pressure side condenser 22 and the low pressure side condenser 2 becomes large (for example, 50 mmHg). ), The water level of the condensate reservoir 7 of the low-pressure condenser 2 becomes high, and the low-pressure side cooling pipe group 5 located above the pressure partition 4 may be submerged in the condensate reservoir 7. is there.

Therefore, as shown in FIG. 6, the pressure partition 4a part 4a of the low pressure side condenser 2 is lowered by, for example, about 50 cm to the reheating chamber 6 side to increase the volume of the condensate reservoir 7, thereby reducing the low pressure side cooling. Measures are taken to prevent the tube group (not shown) from being submerged in the condensate reservoir 7. However, when the part 4a of the pressure partition 4 is lowered to the reheating chamber 6 in this way, the distance from the part 4a of the pressure partition 4 having the perforations 8 to the tray 9 is shortened, and the low pressure side flowing down. There was a problem that the gas-liquid contact time between the condensate and the high-pressure side steam was shortened and the reheating efficiency was lowered.

On the other hand, when the low-pressure side cooling pipe group is provided on the upper side so as to be separated from the condensate pool without lowering a part of the pressure partition wall to the reheating chamber side, there is a problem that the entire condenser is enlarged. .

The present invention has been made in view of the above circumstances, and provides a multistage pressure condenser capable of further improving the reheat efficiency without increasing the size, and a steam turbine plant including the same. is there.

In order to solve the above problems, the present invention employs the following means.
The multi-stage pressure condenser according to the first aspect of the present invention includes a plurality of chambers having different pressures, a pressure partition having a plurality of holes dividing the low-pressure chamber, which is the low-pressure side chamber, in the vertical direction, and the pressure Cooling provided at the upper part of the low-pressure chamber partitioned by a partition wall, where cooling water is introduced and heat-exchanged with the low-pressure side steam led to the low-pressure chamber to condense the low-pressure side steam into the low-pressure side condensate A reheating chamber in which the low-pressure side condensate flowing down from the hole of the pressure partition is accumulated, and a high-pressure chamber that is the chamber on the high-pressure side. A high-pressure-side steam introducing means for introducing the high-pressure-side steam into the reheating chamber, and parallel to each other along the flow-down direction of the low-pressure side condensate flowing down from the hole of the pressure partition below the pressure partition. A plurality of plate-like members disposed, each plate-like member having a front The flow-down direction of the low pressure side condensate cross-section and forms at least one concavo-convex shape.

The low-pressure side condensate flowing down from the hole in the pressure partition comes into gas-liquid contact with the high-pressure side steam introduced into the reheating chamber when flowing down. The longer the gas-liquid contact time, the more the low pressure side condensate is heated.

Therefore, in the present invention, a plurality of plate-like members arranged in parallel to each other along the flow-down direction of the low-pressure side condensate flowing down from the holes of the pressure partition walls are provided below the pressure partition walls. The cross section in the flow-down direction of the low-pressure side condensate is designed to form at least one uneven shape. Thereby, the area which the low pressure side condensate flowing down from the hole of a pressure partition contacts a plate-shaped member can be increased. Therefore, the gas-liquid contact time between the high-pressure side steam introduced into the reheat chamber and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be easily increased without changing the overall size of the multistage pressure condenser.

Also, since a plate-like member is used, the manufacturing cost is low and installation is easy. Therefore, the increase in the manufacturing cost and manufacturing time of the multistage pressure condenser can be suppressed.

In the multistage pressure condenser according to the first aspect of the present invention, it is preferable that the distance between the plate-like members arranged in parallel to each other is variable.

By making the distance between the plate-like members variable, the low-pressure side condensate flowing between the plate-like members is adjusted to flow down and the low-pressure side condensate flowing down is brought into contact with both plate-like members, The flow rate can be controlled. Therefore, the gas-liquid contact time and contact area between the high-pressure side steam and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be increased without changing the size of the multistage pressure condenser.

In the multistage pressure condenser according to the first aspect of the present invention, it is preferable that the plate-like member is porous.

A plate-like member having porosity is used. Thereby, the low-pressure side condensate flowing down along the plate-like member can be dispersed and refined, and the high-pressure side steam can also pass between the plate-like members. Therefore, the gas-liquid contact area between the high-pressure side steam and the low-pressure side condensate can be increased.
Moreover, the manufacturing cost can also be suppressed by utilizing (processing) the existing punching metal material for the plate-like member having the perforations.

In the multistage pressure condenser according to the first aspect of the present invention, it is preferable that the plate-like member has a pocket portion that opens toward the low-pressure side condensate flowing down along the plate-like member.

It was decided to use a plate-like member having a pocket portion that opens toward the low-pressure side condensate that flows down. Thereby, the low-pressure side condensate flowing down along the plate-like member can be temporarily stored in the pocket portion. Therefore, the low-pressure side condensate can be stirred and flowed down in the pocket portion. Accordingly, the reheat efficiency can be increased by increasing the contact area between the high-pressure side steam and the low-pressure side condensate.

Moreover, the plate-shaped member provided with a pocket part exists as a ready-made product. Therefore, an increase in the manufacturing cost of the multistage pressure condenser can be suppressed.

In the multistage pressure condenser according to the first aspect of the present invention, it is preferable that a receiving member for storing and overflowing the low-pressure side condensate flowing down from the plate member is provided below the plate member. .

A receiving member for storing and overflowing the low-pressure condensate flowing down from the plate-like member is provided below the plate-like member. For this reason, the low-pressure side condensate that has overflowed and flowed down from the receiving member creates a circulating flow in the low-pressure side condensate stored in the reheating chamber, and contacts the high-pressure side steam introduced into the reheating chamber over a wide area. Will be. Therefore, the reheat efficiency can be increased.

In the multistage pressure condenser according to the first aspect of the present invention, it is preferable that a part of the pressure partition is provided with a depression in the lower part.

When the pressure difference between the high-pressure chamber and the low-pressure chamber becomes large, the water level of the low-pressure condensate condensed by the cooling pipe group in the low-pressure chamber and stored above the pressure partition rises, and the cooling pipe group is submerged. Fear arises.

Therefore, a part of the pressure partition where the plate-like member is provided is depressed downward. Therefore, it is possible to increase the volume of the low-pressure condensate stored above the pressure partition while maintaining the distance between the lower stage of the cooling pipe group and the water surface of the low-pressure condensate stored above the pressure partition. In addition, since the pressure partition is recessed downward, the distance between the pressure partition and the bottom surface of the reheating chamber is shortened. However, since the plate-like member provided in the pressure partition has at least one uneven shape, the gas-liquid contact time is reduced. Can be maintained. Therefore, the cooling pipe group can be prevented from being submerged when the pressure difference between the high pressure chamber and the low pressure chamber is large, and the reheat efficiency can be maintained without changing the overall size of the multistage pressure condenser.

A steam turbine plant according to the second aspect of the present invention includes the multi-stage pressure condenser as described above.

多 We decided to use a multi-stage pressure condenser that can improve the reheat efficiency without changing the overall size. Therefore, the plant efficiency can be improved without changing the overall arrangement and size of the steam turbine plant.

According to the above-described multistage pressure condenser of the present invention and the steam turbine plant equipped with the same, a plurality of plate-like shapes arranged in parallel to each other along the flow direction of the low-pressure side condensate flowing down from the hole of the pressure partition wall. The member is provided below the pressure partition, and the cross section in the flow direction of the low-pressure side condensate of each of the plate-like members forms at least one uneven shape. Thereby, the area which the low pressure side condensate flowing down from the hole of a pressure partition contacts a plate-shaped member can be increased. Therefore, the gas-liquid contact time between the high-pressure side steam introduced into the reheat chamber and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be easily increased without changing the overall size of the multistage pressure condenser.

Also, since a plate-like member is used, the manufacturing cost is low and installation is easy. Therefore, the increase in the manufacturing cost and manufacturing time of the multistage pressure condenser can be suppressed.

It is a schematic block diagram of the multistage pressure condenser which concerns on 1st Embodiment of this invention. It is a partial expansion schematic block diagram of the low voltage | pressure side condenser of the multistage pressure condenser which concerns on 3rd Embodiment of this invention. It is a partial schematic block diagram of the low voltage | pressure side condenser of the multistage pressure condenser which concerns on 4th Embodiment of this invention. It is a perspective view of the corrugated sheet of the low pressure side condenser of the multi stage pressure condenser concerning a 5th embodiment of the present invention. It is a schematic block diagram of the conventional multistage pressure condenser. It is a schematic block diagram of the modification of the low voltage | pressure side condenser of the multistage pressure condenser shown in FIG.

[First Embodiment]
Hereinafter, the multistage pressure condenser according to the present invention will be described with reference to FIG.
The schematic block diagram of the multistage pressure condenser which concerns on this embodiment is shown by FIG.
The steam turbine plant (not shown) having the illustrated multistage pressure condenser 1 mainly includes a steam turbine (not shown), the multistage pressure condenser 1, and a boiler (not shown). It is configured.

In the steam turbine plant, the steam that has finished the expansion work in the steam turbine is introduced from the steam turbine to the multistage condenser 1 and cooled by the multistage condenser 1 to be condensed and condensate. The condensed water condensed in the multistage condenser 1 is heated by a feed water heater (not shown) and then supplied to the boiler. The condensate supplied to the boiler is converted into steam and used as a drive source for the steam turbine.

As shown in FIG. 1, the multi-stage pressure condenser 1 has a plurality of chambers having different pressures, a high pressure side condenser (high pressure chamber) 22 which is a high pressure side chamber, and a low pressure which is a low pressure side chamber. A side condenser (low pressure chamber) 2 is provided.

The high-pressure side condenser 22 has a high-pressure side cylinder 23 which is a high-pressure side chamber, and a high-pressure side cooling pipe group 25 provided in the high-pressure side cylinder 23.

The low pressure side condenser 2 has a low pressure side cylinder 3 which is a low pressure side chamber, and a low pressure side cooling pipe group (cooling pipe group) 5 provided in the low pressure side cylinder 3.

The low-pressure condenser 2 is divided by a pressure partition 4 that divides the low-pressure condenser 2 in the vertical direction and has a plurality of holes 8. The pressure partition 4 is provided so that the distance between the lower surface of the pressure partition 4 and the bottom surface of the low-pressure side body 3 is, for example, 1000 mm. A low pressure side cooling pipe group 5 is provided on the upper portion of the low pressure side condenser 2 partitioned by the pressure partition 4. In addition, a reheating chamber 6 is provided at the lower part of the low pressure side condenser 2 partitioned by the pressure partition 4.

Cooling water is introduced into the low-pressure side cooling pipe group 5 provided on the upper side of the low-pressure side condenser 2. The cooling water introduced into the low-pressure side cooling pipe group 5 condenses the low-pressure side steam led to the low-pressure side condenser 2 into condensate (hereinafter referred to as “low-pressure side condensate”).

The pressure partition 4 is a perforated plate. The plurality of holes 8 provided in the pressure partition 4 are flow-down holes, and flow down the low-pressure side condensate condensed on the upper side of the low-pressure side condenser 2 to the reheat chamber 6.

Below the pressure partition 4 (on the reheating chamber 6 side), a corrugated plate (plate-shaped member) is disposed along the flow direction of the low-pressure side condensate flowing down from the hole 8 provided in the pressure partition 4. 10 is provided. A plurality of corrugated plates 10 are provided and arranged in parallel to each other.

As shown in FIG. 1, the corrugated plate 10 has an uneven shape (zigzag shape) in which a cross section in the flow direction of the low-pressure side condensate alternately forms a plurality (at least one) of valleys. That is, it is a shape in which peaks and valleys formed on the left and right are repeated along the vertical direction. The corrugated plate 10 is manufactured to have a thickness of 3 mm by SUS304, for example. The corrugated plates 10 arranged in parallel to each other below the pressure bulkhead 4 to form a corrugated plate group are arranged with an interval of about 5 mm, for example, 100 pieces are provided.

A tray (receiving member) 9 is provided below the lower end of the plurality of corrugated plates 10 and in the lower part of the reheating chamber 6. The tray 9 is provided such that its lower surface is at a distance of, for example, about 200 mm from the bottom surface of the low-pressure side barrel 3. In the tray 9, the low-pressure side condensate flows down from the corrugated plate 10. The low-pressure side condensate flowing down to the tray 9 is collected (stored) in the tray 9 and overflows from the tray 9 and falls.

Next, a flow in which steam is condensed by the multi-stage pressure condenser 1 configured as described above to be condensed is described with reference to FIG.
For example, seawater is supplied as cooling water to the low-pressure side cooling pipe group 5 provided in the low-pressure condenser 2. Seawater supplied to the low-pressure side cooling pipe group 5 is sent from a connecting pipe (not shown) to the high-pressure side cooling pipe group 25 of the high-pressure side condenser 22. Seawater sent to the high-pressure side cooling pipe group 25 is discharged from a discharge pipe (not shown).

The low pressure side steam exhausted after finishing the work in the steam turbine is guided to the upper part of the low pressure side condenser 2. The low-pressure side steam led to the upper part of the low-pressure side condenser 2 is condensed by being cooled by the low-pressure side cooling pipe group 5 in which seawater is led into each pipe. It is said. The low-pressure side condensate thus condensed is stored in the upper part of the low-pressure side condenser 2 (above the pressure bulkhead 4 in FIG. 1) to form a condensate pool 7. When the pressure difference between the high pressure side condenser 22 and the low pressure side condenser 2 is, for example, 18 mmHg, the distance between the water surface of the condensate pool 7 and the lowest stage of the low pressure side cooling pipe group 5 is a predetermined value. The distance is about 30 cm.

Since the pressure partition 4 is provided with a plurality of holes 8, the low-pressure side condensate accumulated in the condensate reservoir 7 flows down from the holes 8. The low-pressure condensate flowing down (passing through) the holes 8 flows along the surfaces of the plurality of corrugated plates 10 provided below the pressure partition 4.

On the other hand, the high pressure side steam exhausted after finishing the work in the steam turbine is guided into the high pressure side condenser 22. The high-pressure side steam introduced into the high-pressure side condenser 22 is condensed by being cooled by the high-pressure side cooling pipe group 25 in which seawater is introduced into each pipe (hereinafter referred to as “high-pressure side condensate”). And stored in the high pressure side condenser 22.

Since the high pressure side condenser 22 and the reheating chamber 6 of the low pressure side condenser 2 are connected by a steam duct (high pressure side steam introducing means) 11, the high pressure side steam in the high pressure side condenser 22 is It will be introduced into the reheating chamber 6 from the steam duct 11.

The high-pressure side steam introduced into the reheating chamber 6 makes gas-liquid contact with the low-pressure side condensate flowing down from the pressure partition 4 along the surface of the corrugated plate 10. The low-pressure condensate flowing down along the surface of the corrugated sheet 10 is collected on the tray 9 from the lower end of the corrugated sheet 10.

The low-pressure side condensate collected in the tray 9 overflows from the tray 9 and falls. The low-pressure side condensate dropped from the tray 9 is accumulated in the reheat chamber 6.

In the lower part of the reheating chamber 6, a confluence section (not shown) is provided. A bypass connecting pipe 12 as a bypass means connects to the lower part of the high pressure side condenser 22 at the junction. The high-pressure side condensate stored in the high-pressure side condenser 22 is led to the merging portion via the bypass connecting pipe 12 and merged with the low-pressure side condensate to be condensed. The condensate merged at the merge section is sent to a feed water heater by a condensate pump (not shown).

Since the high-pressure side condensate led from the bypass connecting pipe 12 to the junction is bypassed the low-pressure side condensate stored in the reheat chamber 6 and led to the junction, The high pressure side condensate can be merged into the condensate while keeping the temperature high. Therefore, high-temperature condensate can be sent out from the condensate pump.

In the multistage pressure condenser 1 of the present embodiment, the corrugated plate 10 has a plurality of concave and convex shapes. The time for movement (fluidization) increases. Therefore, the time during which the low-pressure side condensate flowing down the surface of the corrugated plate 10 and the high-pressure side steam come into gas-liquid contact increases. Since the time during which the low-pressure condensate flowing down and the high-pressure steam come into gas-liquid contact increases, the temperature of the low-pressure condensate heated by the high-pressure steam is higher than when the corrugated plate 10 is not used. Become.

Further, the low-pressure side condensate flowing down from the corrugated plate 10 to the tray 9 is heated to a higher temperature while being in gas-liquid contact with the high-pressure side steam while being collected in the tray 9. Further, the low-pressure side condensate falling from the tray 9 causes a circulation flow in the low-pressure side condensate stored in the reheat chamber 6. Therefore, the surface of the low-pressure side condensate and the high-pressure side steam come into contact with each other over a wide area to cause surface turbulent heat transfer and heat the condensate.

Thus, the increase in the gas-liquid contact time between the low-pressure side condensate flowing down along the surface of the corrugated plate 10 and the high-pressure side steam, and the gas between the low-pressure side condensate and the high-pressure side steam collected in the tray 9 are as follows. By the liquid contact and the surface turbulent heat transfer with the high-pressure side steam caused by the low-pressure side condensate overflowing from the tray 9, the condensate is efficiently heated by performing good heat transfer.

Therefore, the condensate can be heated sufficiently without changing the distance at which the low-pressure side condensate falls, that is, the distance between the pressure partition 4 and the bottom surface of the low-pressure side barrel 3. Therefore, the reheat efficiency can be further improved without increasing the size of the multistage pressure condenser 1.

As described above, according to the multistage pressure condenser 1 and the steam turbine plant including the multistage pressure condenser 1 according to the present embodiment, the following operational effects can be obtained.
100 corrugated plates (plate members) 10 disposed in parallel with each other along the flow direction of the low-pressure condensate flowing down from the hole 8 of the pressure partition 4 are provided below the pressure partition 4. The cross section of each corrugated plate 10 in the flow-down direction of the low-pressure condensate forms a plurality (at least one) of uneven shapes. Thereby, the area where the low pressure side condensate flowing down from the hole 8 of the pressure partition 4 contacts the corrugated plate 10 can be increased. Therefore, the gas-liquid contact time between the high-pressure side steam introduced into the reheating chamber 6 and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be easily increased without changing the overall size of the multistage pressure condenser 1.

Further, since the corrugated plate 10 is used, the manufacturing cost is low and the installation is easy. Therefore, an increase in manufacturing cost and manufacturing time of the multistage pressure condenser 1 can be suppressed.

A tray (receiving member) 9 that stores and overflows the low-pressure condensate flowing down from the corrugated plate 10 is provided below the lower end of the corrugated plate 10. Therefore, the low-pressure side condensate that has overflowed and flowed down from the tray 9 causes a circulation flow in the low-pressure side condensate stored in the reheat chamber 6, and the high-pressure side steam introduced into the reheat chamber 6 and a large area. Will come in contact. Therefore, the reheat efficiency can be increased.

多 We decided to use the multi-stage pressure condenser 1 that can improve the reheat efficiency without changing the overall size. Therefore, plant efficiency can be improved without changing the overall arrangement and size of the steam turbine plant (not shown).

In the present embodiment, the multi-stage pressure condenser 1 has been described using a two-stage condenser having the high-pressure condenser 22 and the low-pressure condenser 2, but the present invention is not limited to this. For example, it may be a condenser having three stages of a high pressure side condenser, an intermediate pressure side condenser, and a low pressure side condenser. In this case, the corrugated plate is installed below the pressure partition provided in the intermediate pressure side condenser and the low pressure side condenser.

[Second Embodiment]
The multistage pressure condenser of this embodiment and the steam turbine provided with the same are different from the first embodiment in that the distance between the corrugated plates is variable, and the others are the same. Therefore, about the same structure, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

The distance between corrugated plates (plate-like members) provided in parallel to each other is provided so as to be adjustable. For example, by changing the distance between the corrugated plates from about 5 mm described in the first embodiment to about 2 mm, the falling film thickness of the low-pressure condensate flowing down between the corrugated plates can be adjusted. The flow rate of the side condensate can be reduced.

Since the flow speed of the low-pressure side condensate flowing down the surface of the corrugated sheet can be reduced without changing the length of the extension direction between the corrugated sheets (the flow direction of the low-pressure side condensate), the multistage pressure condenser The gas-liquid contact time between the low-pressure side condensate and the high-pressure side steam can be increased without changing the size of.

As described above, the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
By making the distance between the corrugated plates (plate-like members) variable, the low-pressure side condensate flowing between the corrugated plates is adjusted by adjusting the flow thickness of the low-pressure condensate to contact both corrugated plates. And the flow rate can be controlled. Therefore, the gas-liquid contact time and contact area between the high-pressure side steam and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be increased without changing the size of the multistage pressure condenser.

[Third Embodiment]
The multi-stage pressure condenser of this embodiment and the steam turbine including the same are different from those of the first embodiment in that they have a pocket portion that opens toward the low-pressure side condensate where the corrugated plate flows down, and the others are the same. It is. Therefore, about the same structure, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

FIG. 2 shows a partially enlarged schematic configuration diagram of the low pressure side condenser of the multistage pressure condenser according to the present embodiment.
The corrugated plate 20 has a concavo-convex shape (zigzag shape) in which the cross-section in the flow-down direction of the low-pressure condensate alternately forms a plurality (at least one) of valleys and is as shown in FIG. The concavo-convex convex portion has a pocket portion 21 that opens toward the low-pressure side condensate flowing down along the surface of the corrugated plate 20.

The low-pressure side condensate that flows down along the surface of the corrugated plate 20 from the hole 8 provided in the pressure partition 4 reaches the convex portion of the concavo-convex shape. Since the convex portion is provided with the pocket portion 21 that opens toward the flow-down direction of the low-pressure side condensate, the low-pressure side condensate flows into the pocket portion 21.

The low-pressure side condensate accumulated in the pocket portion 21 overblows from the pocket portion 21 and flows down along the surface of the concave portion of the corrugated plate 20 below the pocket portion 21. In this way, the low-pressure side condensate flowing down from the hole 8 provided in the pressure partition 4 is guided from the surface of the convex portion of the corrugated plate 20 to the pocket portion 21 and overflows from the pocket portion 21 to form a concave portion. It is repeated that it flows down along the surface of the sheet and falls onto the tray (receiving member) 9.

The low-pressure side condensate guided to the pocket portion 21 from the surface of the convex portion of the corrugated plate 20 agitates the low-pressure side condensate stored in the pocket portion 21. Therefore, the contact area between the low pressure side condensate and the high pressure side steam increases. As a result, it is possible to efficiently raise the temperature of the low-pressure side condensate flowing down the corrugated plate 20 through good heat transfer.

As described above, the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
The corrugated plate (plate-shaped member) 20 provided with the pocket portion 21 opened toward the low-pressure side condensate flowing down is used. As a result, the low-pressure side condensate flowing down along the corrugated plate 20 can be temporarily stored in the pocket portion 21. Therefore, the low pressure side condensate can be stirred and flowed down in the pocket portion 21. Therefore, the gas-liquid contact area between the high-pressure side steam and the low-pressure side condensate can be increased.

Moreover, the corrugated sheet 20 provided with the pocket part 21 exists as a ready-made product. Therefore, an increase in the manufacturing cost of a multistage pressure condenser (not shown) can be suppressed.

[Fourth Embodiment]
The multi-stage pressure condenser of this embodiment and the steam turbine equipped with the same are different from the first embodiment in that a part of the pressure bulkhead provided with the corrugated plate is recessed downward, and the others are the same. It is. Therefore, about the same structure, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

The partial schematic block diagram of the low voltage | pressure side condenser of the multistage pressure condenser which concerns on this embodiment is shown by FIG.
In the pressure partition wall 34, a part 34 a where the corrugated plate (plate-like member) 10 is provided is depressed downward to form a condensate reservoir 37. While the distance between the pressure partition wall 34 and the bottom surface of the low-pressure side body (not shown) is, for example, 1000 mm, a part 34a of the pressure partition wall 34 is formed to be recessed downward, for example, by about 500 mm.

When the pressure difference between the high pressure side condenser (high pressure chamber) and the low pressure side condenser (low pressure chamber) 2 constituting the multistage pressure condenser (not shown) becomes large (for example, 50 mmHg) In this case, the amount of low-pressure condensate collected above the pressure partition 34 increases. The increased low-pressure side condensate accumulates in a part 34 a of the pressure partition wall 34 to form a condensate pool 37. Therefore, the distance between the lowermost stage of the low-pressure side cooling pipe group (cooling pipe group) and the water surface of the condensate pool 37 can be maintained at a predetermined distance (about 30 cm).

As a result, the pressure difference between the high pressure side condenser (not shown) and the low pressure side condenser 2 is increased, and the amount of low pressure side condensate is increased, so that the low pressure side condensate accumulated above the pressure partition 34 is increased. It is possible to prevent the low pressure side cooling pipe group (not shown) from being submerged.

Also, a plurality of corrugated plates 10 are provided below a part 34 a of the pressure partition 34 forming the condensate pool 37. Therefore, when the corrugated plate 10 is not provided even if the flow length in the extending direction of the corrugated plate 10 (the flow direction of the low-pressure side condensate) is shortened due to the depression 34a of the pressure partition wall 34 being depressed downward. As compared with the above, the gas-liquid contact time between the low-pressure side condensate and the high-pressure side steam can be lengthened to raise the temperature of the low-pressure side condensate.

As described above, the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
A part 34a of the pressure partition wall 34 in which the corrugated plate (plate-like member) 10 is provided below the pressure partition wall 34 is recessed downward. Therefore, the volume of the condensate sump 37 in which the low-pressure side condensate stored above the pressure partition 34 is stored can be increased. In addition, since the portion 34a of the pressure partition 34 is recessed downward, the distance between the portion 34a of the pressure partition 34 and the bottom surface of the reheating chamber 6 is shortened, but provided below the portion 34a of the pressure partition 34. Since the corrugated sheet 10 has a plurality of (at least one) irregular shapes, the gas-liquid contact time can be maintained. Therefore, when the pressure difference between the high pressure side condenser (high pressure chamber) and the low pressure side condenser (low pressure chamber) 2 is large, the low pressure side cooling pipe group (cooling pipe group) is prevented from being submerged, and the multistage pressure recovery is performed. Reheating efficiency can be maintained without changing the overall size of the water vessel (not shown).

[Fifth Embodiment]
The multistage pressure condenser of this embodiment and the steam turbine provided with the same are different from those of the fourth embodiment in that the corrugated plate is porous, and the others are the same. Therefore, about the same structure, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

FIG. 4 is a perspective view of the corrugated plate of the low pressure side condenser of the multistage pressure condenser according to the present embodiment.
The corrugated plate 40 has a concavo-convex shape (zigzag shape) in which the cross section in the flow direction of the low-pressure condensate (shown by the white arrow in FIG. 4) alternately forms a plurality (at least one) of valleys. In addition, as shown in FIG.

The low-pressure side condensate flowing along the surface of the corrugated plate 40 from a hole (not shown) provided in a part 34a (see FIG. 3) of the pressure partition wall 34 reaches the corrugated plate 40 surface. Since the corrugated plate 40 has a perforation 41 and is open, the low-pressure side condensate flows down the corrugated plate 40 and the perforated 41 and flows into the adjacent corrugated plate 40 surface. It will be a thing.

By repeating this, the low-pressure side condensate falls to the tray (receiving member) 9 (see FIG. 3).
The low-pressure side condensate flowing down into the perforations 41 of the corrugated plate 40 is dispersed and refined on the adjacent corrugated plate 40 surface. Further, the high-pressure side steam also passes through the perforations 41 as indicated by dotted arrows in FIG. Therefore, the contact area between the low pressure side condensate and the high pressure side steam increases. Thereby, good heat transfer is performed and the low-pressure side condensate flowing down the corrugated plate 40 can be efficiently heated.

As described above, the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
The corrugated plate (plate member) 40 provided with the perforations 41 toward the low-pressure side condensate flowing down was used. Thereby, the low-pressure side condensate flowing down along the corrugated plate 40 can be dispersed and refined, and the high-pressure side steam can also pass between the corrugated plates 40. Therefore, the gas-liquid contact area between the high-pressure side steam and the low-pressure side condensate can be increased.
For the corrugated plate 40 having the perforations 41, the manufacturing cost can be reduced by using (processing) the existing punching metal material.

It should be noted that the present invention is not limited to the above-described embodiment, and can be changed as appropriate without departing from the scope of the invention.

1 Multi-stage pressure condenser 2 Low pressure condenser (low pressure chamber)
4 Pressure bulkhead 5 Low pressure side cooling pipe group (cooling pipe group)
6 Reheating chamber 8 Hole 9 Tray (receiving member)
10 Corrugated plate (plate-like member)
11 Steam duct (high-pressure side steam introduction means)
22 High pressure condenser (high pressure chamber)
41 porous

Claims (7)

Multiple chambers with different pressures;
A pressure partition having a plurality of holes dividing the low-pressure chamber, which is the chamber on the low-pressure side, in the vertical direction;
Provided in the upper part of the low-pressure chamber partitioned by the pressure partition, the low-pressure side steam is condensed into the low-pressure side condensate by introducing cooling water and exchanging heat with the low-pressure side steam guided to the low-pressure chamber. Cooling tube group to be
A lower part of the low-pressure chamber partitioned by the pressure partition, and a reheat chamber in which the low-pressure side condensate flowing down from the hole of the pressure partition is accumulated;
High pressure side steam introducing means for introducing high pressure side steam in the high pressure chamber, which is the chamber on the high pressure side, into the reheating chamber;
Below the pressure partition, a plurality of plate-like members arranged in parallel with each other along the flow-down direction of the low-pressure side condensate flowing down from the hole of the pressure partition,
Each of the plate-like members is a multistage pressure condenser in which a cross section in the flow-down direction of the low-pressure side condensate forms at least one uneven shape. The multi-stage pressure condenser according to claim 1, wherein a distance between the plate-like members arranged in parallel to each other is variable. The multi-stage pressure condenser according to claim 1 or 2, wherein the plate-like member has a perforation. The multi-stage pressure condenser according to any one of claims 1 to 3, wherein the plate-like member includes a pocket portion that opens toward the low-pressure side condensate flowing down along the plate-like member. The multistage pressure condenser according to any one of claims 1 to 4, wherein a receiving member for storing and overflowing the low-pressure side condensate flowing down from the plate-like member is provided below the plate-like member. The multi-stage pressure condenser according to any one of claims 1 to 5, wherein a part of the pressure partition wall provided with the plate-like member is recessed downward. A steam turbine plant comprising the multi-stage pressure condenser according to any one of claims 1 to 6.

Images